US4419571A - Stepped-down mechanical counting mechanism - Google Patents

Stepped-down mechanical counting mechanism Download PDF

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Publication number
US4419571A
US4419571A US06/368,206 US36820682A US4419571A US 4419571 A US4419571 A US 4419571A US 36820682 A US36820682 A US 36820682A US 4419571 A US4419571 A US 4419571A
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Prior art keywords
control disc
notch
wheels
notches
advancing
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US06/368,206
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English (en)
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Ulf Koch
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Esselte Pendaflex Corp
ESSELTE PENDEFLEX Corp
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ESSELTE PENDEFLEX Corp
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41K—STAMPS; STAMPING OR NUMBERING APPARATUS OR DEVICES
    • B41K3/00—Apparatus for stamping articles having integral means for supporting the articles to be stamped
    • B41K3/02—Apparatus for stamping articles having integral means for supporting the articles to be stamped with stamping surface located above article-supporting surface
    • B41K3/04—Apparatus for stamping articles having integral means for supporting the articles to be stamped with stamping surface located above article-supporting surface and movable at right angles to the surface to be stamped
    • B41K3/10—Apparatus for stamping articles having integral means for supporting the articles to be stamped with stamping surface located above article-supporting surface and movable at right angles to the surface to be stamped having automatic means for changing type-characters, e.g. numbering devices
    • B41K3/102—Numbering devices
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06M—COUNTING MECHANISMS; COUNTING OF OBJECTS NOT OTHERWISE PROVIDED FOR
    • G06M1/00—Design features of general application
    • G06M1/04—Design features of general application for driving the stage of lowest order
    • G06M1/041—Design features of general application for driving the stage of lowest order for drum-type indicating means

Definitions

  • the invention relates to a stepped-down mechanical counting mechanism, in which number wheels are mounted on a locking shaft so as to adjoin one another without a gap, and a control disc is connected in front of the units wheel, the number wheels and control disc being driven by a ratchet shaft which is located in the interior of the locking shaft and rotates to and fro through a working angle and to which are articulated spring-loaded pawls each acting on one pair of wheels.
  • Such a counting mechanism is described as the first exemplary embodiment of German patent application No. P 3001321.9and correspnding U.S. Pat. No. 4,343,238. It serves as a printing mechanism for consecutive, preferably decimal numbering and is designed, likewise, for direct as well as stepped-down advancing.
  • Such a counting mechanism can be used, in particular, in a hand labelling machine. Direct advancing is employed when individual articles are to be marked with consecutively numbered labels. In this switching mode, referred to below as mode M1, an advancing movement of the number wheel of the lowest numerical place (units wheel) therefore takes place during each stroke of the ratchet shaft. On the other hand, if pairs of articles are to be marked, two identical labels have to be printed.
  • the abovementioned counting mechanism also operates with multiple or repeated switching which provides for two (M3), three (M4) or even more idle strokes between two switching strokes. Moreover, it is known to stop completely the advancing of the counting mechanism (switching mode M0).
  • the desired switching mode is predetermined by the graduation of a control disc.
  • a particular control disc which is built fixedly into the machine is necessary for each switching mode.
  • a counting mechanism is produced having a quite definite switching mode which cannot be changed directly by the user.
  • the object of the invention is to remedy this deficiency and to provide a counting mechanism of the type mentioned in the introduction, which permits an alteration of the switching mode by a simple change-over and, in particular, a preselection of no (M1), one (M2), two (M3) or three (M4) idle strokes between two switching strokes moving the counting mechanism.
  • M1 no
  • M2 one
  • M3 two
  • M4 idle strokes between two switching strokes moving the counting mechanism.
  • control disc can be advanced by means of an idle-stroke pawl subjected to the action of an adjustable slotted link and, independently thereof, by means of an advancing pawl acting between the control disc and the units wheel.
  • a stepped-down counting mechanism in which the switching mode can be preselected by adjusting a slotted link.
  • the counting mechanism according to the invention in a hand labelling machine, can replace several of the printing mechanisms having a fixed switching mode, which are required according to the state of the art.
  • the invention can also be applied advantageously in other counting or numbering machines.
  • FIG. 1 shows a view in a longitudinal section through the counting mechanism
  • FIG. 2 shows a partial side view of the counting mechanism
  • FIG. 3 shows a plan view of a number wheel of the counting mechanism
  • FIG. 4 shows a side view in a cross-section along the line A-B of FIG. 3;
  • FIG. 5 shows a plan view of the control disc of the counting mechanism
  • FIG. 6 shows a side view in a cross-section along the line C-D of FIG. 5;
  • FIG. 7 shows an enlarged front view of the idle-stroke pawl
  • FIG. 8 shows a side view of the idle-stroke pawl in the direction "E" of FIG. 7;
  • FIG. 9 shows a plan view of the slotted link of the counting mechanism
  • FIG. 10 shows a side view in a cross-section along the line F-G of FIG. 9.
  • FIGS. 11 to 15 show diagrams illustrating the position of the slotted link and the control disc after switching of the units wheel, specifically
  • FIG. 11 for switching mode M2
  • FIG. 12 for switching mode M3
  • FIG. 13 for switching mode M4
  • FIG. 14 for switching mode M0
  • the counting mechanism 1 advancing by decimal places is combined with number wheels 2 which are adjustable exclusively by hand.
  • This arrangement is used in labelling machines in which a label is printed with a permanently predetermined mark and, at the same time, with a serial number.
  • the manually adjustable number wheels 2 are drawn, together with number wheels 3 advancing by decimal places, a control disc 4 and a slotted link 5, on a common locking shaft 6.
  • the control disc 4 is located in front of the units wheel 3a, that is to say, the lowest placed of the advancing number wheels 3.
  • the slotted link 5 is, in turn, connected in front of the control disc 4 on the drive side.
  • the wheels drawn onto the locking shaft that is to say the number wheels 2; 3, the control disc 4 and the slotted link 5, adjoin one another without a gap and are supported laterally against one another. They can be rotated individually independently of one another and are positioned and locked on the locking shaft 6 in angular positions offset to one another one step at a time.
  • the number wheels 2; 3 are gearwheels with an external toothing 7a (see FIG. 3).
  • the slotted link 5 is also provided with an external toothing 7b (see FIG. 9).
  • An adjusting mechanism (not shown) by means of which the number wheels 2; 3 and the slotted link 5 are brought into a pre-selectable position, engages into this external toothing 7a; 7b.
  • the locking shaft 6 is a slotted cylindrical sleeve 8, the outer shell 9 of which constitutes the running face of the number wheels 2, 3, the control disc 4 and the slotted link 5.
  • Said wheels each have a central middle bore 10a; 10b; 10c, the clear width of which corresponds to the diameter of the sleeve 8, and are threaded onto the sleeve 8.
  • the inner ring 11a; 11b; 11c of the middle bore 10a; 10b; 10c is provided, in each case, with a notch. In the case of the manually adjustable number wheels 2, this consists of a single gear rim taking up the full width of the number wheels 2.
  • a gear rim 12a; 12b on the drive side and a gear rim 13a; 13b on the driven side are recessed, in each case, on the inner ring 11a; 11b.
  • the gear rim 12a; 12b on the drive side and the gear rim 13a; 13b on the driven side each take up a part of the width, preferably half the width, of the advancing number wheel 3 and of the control disc 4.
  • the notch on the inner ring 11c of the slotted link 5 is also divided in its width.
  • a locking toothing 12c is provided on the side of the slotted link 5 which faces away from the control disc 4.
  • a guide path 13c applying the effect of the slotted link is shaped on the other side facing the control disc 4. Analogously to the advancing number wheels 3 and the control disc 4, the locking toothing 12c and the guide path 13c preferably take up half the width of the slotted link 5.
  • the notches of the wheels drawn onto the locking shaft 6 interact with a spring comb 14 for positioning the wheels.
  • a front view of the spring comb 14 can be seen from FIG. 1 and a side view from the illustrations of FIG. 2 and FIGS. 11 to 15.
  • the spring comb 14 is located on the outer shell 9 of the sleeve 8 and is partly countersunk into the sleeve 8. It consists of a comb back 15 and leaf springs 16; 16a; 17 projecting from this in the form of prongs.
  • the leaf springs 16; 16a; 17 project over at least part of their length beyond the outer shell 9 of the sleeve 8 and, as a result of radial pressure, can be countersunk into a spring bed 18 underneath the outer shell 9 (see FIG. 2).
  • An individual leaf spring 16; 16a; 17 is provided for each of the wheels on the locking shaft 6.
  • the leaf springs 16 for the number wheels 2; 3 and the leaf spring 16a for the slotted link 5 are designed identically. They each carry at the spring end an individual knob 19.
  • the leaf spring 17 for the control disc 4 is, on the other hand, provided with two knobs 20a; 20b located at a specific distance from one another (see FIGS. 11 to 15). The knobs 19; 20a; 20b drop as a result of spring force into the notches of the wheels and thereby lock the wheels in specific locking positions.
  • the leaf springs 16; 16a; 17 run centrally on the continuous gear rim, in the case of the advancing number wheels 3 and the control disc 4 on the gear rim 12a and 12b respectively on the drive side, and in the case of the slotted link 5 on the locking toothing 12c. This results in an offset of the leaf springs 16; 16a; 17, which leads to the formation of a single larger comb gap 21 at the joint between the manually moved and the advancing number wheels 2 and 3 respectively (see FIG. 1).
  • a ratchet shaft 22 Inserted through the sleeve 8 is a ratchet shaft 22, by means of which the advancing number wheels 3 and the control disc 4 are moved.
  • the ratchet shaft 22 is mounted rotatably in the interior of the sleeve 8. During each stroke of the counting mechanism 1, it is rotated to and fro through a definite working angle ⁇ . In the case of a counting mechanism 1 advancing by decimal places, the switching angle of the number wheels is 36°. Accordingly, the working angle ⁇ of the ratchet shaft 22 must be selected somewhat larger, in order to compensate mechanical tolerances and inaccuracies in the notches. In the present exemplary embodiment, the working angle ⁇ amounts to 40°.
  • Articulated to the ratchet shaft 22 is a series of pawls 23; 23a; 23b; 24, which drop into the notches of the advancing number wheels 3 and of the control disc 4 respectively, and which drive these at a definite switching rhythm.
  • the pawls 23; 23a; 23b; 24 engage through a slot 25 in the sleeve 8 into notches Z; S of the gear rims 12a; 12b; 13a; 13b.
  • Each of these notches Z; S (see FIG. 3) has a steep front side 26 in the advancing direction of the wheels to be moved.
  • each of the pawls 23; 23a; 23b; 24 consists of an essentially cylindrical, centrally perforated jointed body 28 and of a projection 29 which projects radially therefrom and which is designed as the negative form of a notch Z; S.
  • the pawls 23; 23a; 23b; 24 are pushed, by means of the bore 30 of their jointed body 28, next to one another on a pin 31 as a common axle.
  • the pin 31 is retained parallel to the ratchet shaft 22 by means of two carriers 32a; 32b shaped on the ratchet shaft 22 and is connected fixedly to the ratchet shaft 22.
  • the pawls 23; 23a; 23b; 24 can rotate about the pin 31 with a play of movement.
  • the axial centre point of the pin 31 is located so that the outer wall 33 of the jointed body 28 of a pawl 23; 23a; 23b; 24 threaded onto the pin 31 lies within an extended outer peripheral circle of the sleeve 8 (see FIG. 2). Consequently, the pawls 23; 23a; 23b; 24 are countersunk with their jointed bodies 28 below the running face of the wheels.
  • the projection 29 of the pawls 23; 23a; 23b; 24 can likewise be set back below the running face of the wheels as a result of rotation of the pawl 23; 23a; 23b; 24 about the pin 31 (unbroken line in FIG.
  • each individual pawl 23; 23a; 23b; 24 is loaded by the force of a compression spring 34.
  • the compression springs 34 are mounted in suitable blind bores 35 in the ratchet shaft 22. They act upon the projections 29 of the pawls 23; 23a; 23b; 24 in such a way that the pawls 23; 23a; 23b; 24 are rotated about the pin 31 and the projections 29 are pressed radially outwards against the notches of the advancing number wheels 3 and control disc 4 respectively (broken line in FIG. 2).
  • the pawls 23; 23a; 23b; 24 engage on the arc of the working angle ⁇ and move the advancing number wheels 3 and the control disc 4 from locking position to locking position.
  • FIG. 1 shows the arrangement of the pawls 23; 23a; 23b; 24 in relation to the wheels to be moved.
  • a pawl 23a is assigned to each pair of advancing number wheels 3, 3a.
  • the advancing number wheels 3; 3a are drawn onto the locking shaft 6 and are offset to the pawls 23; 23a in such a way that a pawl 23a overlaps the joint between two number wheels 3; 3a.
  • the pawl 23a runs, in each case, with the one half of its width in the gear rim 13a, on the driven side, of a number wheel 3a of a low numerical place and with the other half of its width in the gear rim 12a, on the drive side, of the number wheel 3 of the next higher numerical place.
  • a pawl designated below as an advancing pawl 23b runs with half of its width in the gear rim 13b, on the driven side, of the control disc 4 and the other half runs in the gear rim 12a, on the drive side, of the units wheel 3a.
  • a pawl referred to below as an idle-stroke pawl 24 runs with the one half of its width in the gear rim 12b, on the drive side, of the control disc 4 and with the other half of its width on the guide path 13c of the slotted link 5.
  • FIG. 3 and FIG. 4 show, in the first place, the design of the advancing number wheels 3; 3a.
  • the advancing number wheels 3; 3a are provided, as already mentioned, with an external toothing 7a which permits the engagement of an adjusting mechanism.
  • the inner ring 11a limiting the middle bore 10a has, on the drive side, a gear rim 12a with ten identical notches Z36 arranged at the same angular distance from one another.
  • the gear rim 13a on the driven side consists of a single notch Z0 which is aligned with one of the notches Z36 on the drive side and which thus forms a continuous notch Z0.
  • a pawl 23a working within the decimal counting mechanism runs lifted out, during nine out of ten strokes of the ratchet shaft 22, on the unnotched inner ring 11a of a number wheel 3a of a low numerical place and is engaged into the continuous notch Z0 during only one of ten strokes.
  • a stepping-down ratio of 1:10 and a coupling of the pawls 23; 23a; 23b; 24, which is known from the above-referenced German Patent Specification a decimal advancing of the counting mechanism 1 is achieved.
  • FIG. 5 and FIG. 6 show the control disc 4 of the counting mechanism 1. In contrast to the number wheels 2; 3 and the slotted line 5, this is not moved manually and therefore has an outer contour 36 free of toothing.
  • the inner ring 11b of the control disc 4 is provided with a notch which is divided in its width and which consists of a gear rim 12b on the drive side and of a gear rim 13b on the driven side.
  • the gear rim 13b on the driven side is formed by five 72° notches S72; S72a arranged at angular intervals of 72° from one another.
  • the gear rim 12b on the drive side has, likewise, a five-digit symmetry. It consists of groups of notches which are each assigned to one of the 72° notches S72; S72a of the gear rim 13b on the driven side. Initially, each 72° notch S72; S72a on the drive side is recessed into an incision 37. Thus, the front edge 38 of this incision 37 lies in the extension of the front side 26a of the 72° notch S72; S72a.
  • This guidance of the front edge 38 permits a pivoting movement of the idle-stroke pawl 24 through a relatively large angle into a special deep engagement position. In this position, which is required only for the switching mode M1, a hook 39 shaped on the idle-stroke pawl 24 locks into the incisions 37 (see FIG. 15).
  • the front edge 38 of the incision 37 merges into a plateau 40 which forms a stop for the hook 39.
  • the rear edge 41 of the incision 37 descends parallel to the front edge 38 and at a distance from the latter which corresponds to the width of the hook 39.
  • the rear edge 41 comes up against the rearward side 27a of the 72° notch S72; S72a on the driven side.
  • the gear rim 12b on the drive side follows this side 27a over a short section 42 which is formed over the full width of the control disc 4. Consequently, of the 72° notch S72; S72a, only this short section 42 is present on the drive side of the control disc 4. Further notches then adjoin this length 42 on the drive side.
  • a 12° notch S12, a 24° notch S24 and a 36° notch S36 are located after the 72° notches S72, each at an angular interval of 12°.
  • the 36° notch S36 is designed without the conventional rearward side 27, with only a front side 26b as a stop face in the advancing direction. The outer end of this front side 26b merges into a ring edge 43 without toothing, which extends parallel to the inner ring 11b and which leads onto the incision 37 of the next 72° notch S72a.
  • the leaf spring 17 serving for locking the control disc 4 has two knobs 20a; 20b. Locking positions of the control disc 4 are defined as a result of the engagement of these knobs 20a; 20b into the gear rim 12b on the drive side.
  • the knobs 20a; 20b are engaged offset 36° to one another. Locking positions with the gear rim 12b on the drive side are provided every 12°, as becomes clear from the consideration which follows.
  • the 12° notches S12 and the 24° notches S24 are formed completely in the gear rim 12b on the drive side.
  • the 36° notches S36 and 72° notches S72; S72a are incomplete, and have complementary pieces.
  • the 36° notch S36 has the front side 26b, whereas the 72° notch S72; S72a has a part of the rearward side 27a in the form of the section 42.
  • the leaf spring 17 engages with these incomplete notches in such a way that one knob 20a rests against the section 42 of the 72° notch S72 and the other knob 20b rests against the front side 26b of the 36° notch S36.
  • the recessed incisions 37 on the drive side of the control disc 4 permit a special deep engagement position of the idle-stroke pawl 24.
  • the correspondingly modified form of the idle-stroke pawl 24 is to be seen in the illustrations of FIG. 7 and FIG. 8.
  • the projection 29 of the idle-stroke pawl 24 is provided with a groove 44 which extends from the jointed body 28 close up to the front edge 45 of the projection 29.
  • the remaining piece of the projection 29 forms the hook 39 which can drop into the recessed incisions 37.
  • the groove 44 and the hook 39 take up the half side 46a of the idle-stroke pawl 24 which acts on the control disc 4.
  • the other half side 46b of the idle-stroke pawl 24, running on the slotted link 5, has, on the other hand, the full outer contour of the projection 29.
  • the idle-stroke pawl 24 works freely and independently of the other pawls 23; 23a. Consequently, no further driving devices are provided on the projection 29.
  • all the pawls 23; 23a; 23b; 24 carry on the underside of the projection 29 a peg 47 (not shown in FIG. 2) which serves to guide the compression spring 34.
  • the form of the slotted link 5 can be seen in the illustrations of FIG. 9 and FIG. 10.
  • the slotted link 5 is an adjustable wheel drawn onto the locking shaft 6. It is provided with a continuous external toothing 7b which is illustrated in FIG. 9 only on part of the periphery. There engages into the external toothing 7b an adjusting mechanism (not shown), by means of which the slotted link 5 is rotated into different locking positions. The slotted link 5 is moved only manually, and is consequently not driven by the idle-stroke pawl 24.
  • the inner ring 11c of the slotted link 5 is provided, on the side facing away from the control disc 4, with the locking toothing 12c and, on the side facing the conftrol disc 4, with the guide path 13c.
  • the locking toothing 12c consists of the notches K0, K1, K2, K3 and K4. Locking positions of the slotted link 5 are defined by the engagement of a leaf spring 16a into one of these notches.
  • the engagement position corresponds to a selected switching mode MO (notch K0), M1 (notch K1), M2 (notch K2), M3 (notch K3) or M4 (notch K4).
  • the guide path 13c consists of two curves 48; 49.
  • the two curves 48; 49 each span the full working angle ⁇ of the ratchet shaft 22.
  • a first, shallow curve 48 is assigned to the locking positions in the notches K0, K2, K3 and K4 and to the switching mode M0, M2, M3 and M4.
  • the shallow curve 48 is cut out to such a depth that, although the idle-stroke pawl 24 running thereon engages with the notches S12; S24; S36 of the control disc 4, it nevertheless does not engage with the recessed incisions 37 of the control disc 4.
  • a second, recessed curve 49 is assigned to the locking position in the notch K1, that is to say, the switching mode M1. Its depth is selected so that the idle-stroke pawl 24 can drop with the hook 39 into the recessed incisions 37.
  • the notches K0, K2, K3 and K4 of the slotted link 5 are each arranged at an angular interval of 12° from one another. The reason for this is made clear in the functional description below, with reference to the illustrations of FIGS. 11 to 15.
  • FIGS. 11 to 15 show diagrammatically the relative positions of the control disc 4 and the slotted link 5, in each case after the completion of a switching stroke, by means of which the units wheel 3a of the counting mechanism 1 has been advanced.
  • one of the 72° notches S72 of the control disc 4 stood at the start of the working angle ⁇ and was aligned with one of the ten notches Z36 on the drive side of the units wheel 3a.
  • the advancing pawl 23b it was possible for the advancing pawl 23b to drop, and the control disc 4 and the units wheel 3a were rotated synchronously through 36°.
  • the 72° notch S72 of the control disc thereby reached the position shown in FIGS. 11 to 15, at the end of the working angle ⁇ .
  • the switching mode M2 is preselected. Accordingly, in the starting position described, one idle stroke in which the units wheel 3a of the counting mechanism 1 is not moved must be carried out. According to FIG. 12, the switching mode M3 is preselected as a result of locking of the slotted link 5 in the notch K3. Two idle strokes must therefore take place.
  • FIG. 13 relates, correspondingly, to the switching mode M4 with locking of the slotted link 5 in the notch K4 and three idle strokes. In FIG. 14, the slotted link 5 engages in the notch KO.
  • the advancing of the counting mechanism 1 is, as a result, completely interrupted (switching mode MO), and the counting mechanism 1 remains, over any number of strokes, in the position reached last.
  • switching mode MO switching mode MO
  • advancing without stepping-down is effected as a result of locking of the slotted link 5 in the notch K1 (switching mode M1). Consequently, during each stroke of the ratchet shaft 22, the units wheel 3a of the counting mechanism 1 is moved on one place.
  • FIG. 11 with the switching mode M2 is first considered, the idle-stroke pawl 24 is seen to be engaged with the 36° notch S36 of the control disc 4, which stands at the start of the working angle ⁇ .
  • the idle-stroke pawl 24 rests against the front side 26b which is made complete in the otherwise incomplete 36° notch S36.
  • the shallow curve 48 of the slotted link 5 spans the full arc of the working angle ⁇ and does not limit the switching angle of the idle-stroke pawl 24. Consequently, during the forthcoming stroke of the ratchet shaft 22, the control disc 4 is rotated by the idle-stroke pawl 24 through a full 36° . The advancing pawl 23b is lifted out in this way.
  • the advancing pawl 23b again engages into a 72° S72a of the control disc 4, and the units wheel 3a is switched.
  • the idle-stroke pawl 24 is likewise pivoted, but has no drive function, since the front side of the 72° notch S72; S72a is not shaped on the drive side of the control disc 4. Consequently, in the switching mode M2, the control disc 4 is rotated 36° alternately either by the drive side or by the driven side, the units wheel 3a being moved only during the stroke of the advancing pawl 23b which acts on the driven side.
  • the idle-stroke pawl 24 runs on the shallow curve 48 of the slotted link 5. This has, initially, the function of blocking engagement of the hook 39 shaped on the idle-stroke pawl 24 into the recessed incisions 37 of the control disc 4. The same also applies to the switching modes M0, M3 and M4. Moreover, in the mode M2, the terminal edge 50 of the shallow curve 48 stands at the start of the working angle ⁇ .
  • the slotted link serves to prevent an incorrect enlargement of the switching travel and to compensate possible inaccuracies in the toothing.
  • the slotted link 5 is offset 12° in the advancing direction relative to the mode M2.
  • the corresponding angular interval between the notches K0, K2, K3 and K4 has already been mentioned.
  • the shallow curve 48 of the slotted link 5 therefore spans the working angle ⁇ of the ratchet shaft 22 only over an arc length which shortens the switching angle of the idle-stroke pawl 24 to 24°.
  • FIG. 12 shows, accordingly, the idle-stroke pawl 24 in its earliest possible engagement position.
  • the idle-stroke pawl 24 is prevented, by the terminal edge 50 of the shallow curve 48, from engaging into the 36° notch S36 of the control disc 4 and can drop only as illustrated into the 24° notch S24. Consequently, during the switching operation included in the cycle, the control disc 4 is moved only through a reduced switching angle of 24°.
  • the idle-stroke pawl 24 could engage again, being set back 24°, but encounters no notch at this point. the first possibility of dropping is afforded at the 36° notch S36 of the control disc 4, which now stands 12° before the end of the switching angle ⁇ .
  • a complete stroke of 36° of the control disc 4 together with the units wheel is therefore followed, in the switching mode M3, by two idle strokes through 24° and 12°, which are effected as a result of a reduction of the switching angle to 24° by means of the slotted link 5 and as a result of the incomplete 12° toothing on the drive side of the control disc 4.
  • FIG. 13 illustrates correspondingly the idle-stroke switching for the switching mode M4.
  • the slotted link 5, offset a further 12°, is engaged into the associated notch K4.
  • the switching angle of the idle-stroke pawl 24 is thereby reduced to 12°. Since the toothing, on the drive side, of the control disc 4 has, following the 72° notch S72; S72a, three notches S12, S24 and S36 at intervals of 12°, three idle strokes through 12° are executed, before a renewed switching movement through 36° of the units wheel 3a together with the control disc 4 is carried out.
  • the reduction of the switching angle of the idle-stroke pawl 24 by means of the slotted link 5 in the switching modes M2, M3 and M4 is extended in the switching mode M0 (see FIG. 14).
  • the slotted link is offset a further 12° in the advancing direction.
  • the shallow curve 48 of the slotted link 5 no longer coincides, as a result, with the working angle ⁇ of the ratchet shaft 22.
  • the idle-stroke pawl 24 runs, lifted out, on the inner ring 11c of the slotted link 5 and drops, only as illustrated, at the end of the switching angle ⁇ into one of the 72° notches S72, S72a of the control disc 4. During this time, there is no movement of wheels.
  • the shallow curve 48 of the slotted link 5 limits the depth of insertion of the idle-stroke pawl 24.
  • the hook 39 shaped on the idle-stroke pawl 24 cannot, as a result, drop into the recessed incisions 37 of the control disc 4.
  • This engagement is released in the switching mode M1 (see FIG. 15).
  • the recessed curve 49 is placed above the arc of the working angle ⁇ . In this way, the idle-stroke pawl 24 can pivot epicyclically through a larger angle and can become hooked in the incisions 37.
  • the control disc 4 is coupled by the idle-stroke pawl 24 to the ratchet shaft 22 in both directions of movement. During each stroke of the ratchet shaft 22, the idle-stroke pawl 24 first moves the control disc 4 in a backward direction and then guides it forwards again into the starting position .
  • the advancing pawl 23b Since the recessed incisions 37 are designed as a continuation of the 72° notches S72; S72a, the advancing pawl 23b also drops, at the same time as the locking idle-stroke pawl 24, into the 72° notches S72; S72a. During this time, there is no hooking on the driven side of the control disc 4. Rather, the advancing pawl 23b is lifted out on the inner ring 10a of the units wheel 3a and is made to engage with the respective next notch Z36 of the gear rim 12a on the drive side. In this way, during each stroke of the ratchet shaft 22, the units wheel 3a of the counting mechanism 1 is moved on one place.
  • the control disc 4 is the only wheel of the counting mechanism 1 to execute switching movements in both forward and backward directions.
  • the backward movement via the leaf spring 17 provided with two knobs 20a; 20b is possible without difficulty. It is advantageous for this backward movement if the leaf spring 17 has a greater length and a lesser rigidity than the other springs 16; 16a of the spring comb 14.
  • the locking of the control disc 4 requires less precision than that of the number wheels 2; 3.
  • the switching mode of the counting mechanism 1 can be changed after any stroke of a counting series, since the counting mechanism 1 is realigned automatically. For example, after the second stroke in the mode M4, a changeover to the mode M3 can be made directly. Incorrect movements of the control disc 4 are then to be expected, at most, only until the advancing pawl 23b is ready for engagement for the first time. After the switching of the units wheel 3a together with the control disc 4, which then takes place, the newly selected mode is provided.
  • the realignment of the counting mechanism 1 is achieved due to the fact that, on the drive side of the control disc 4, only the notches absolutely essential for the particular switching mode are recessed.
  • the invention is not restricted to the division described, with a five-digit symmetry and with an incomplete 12° toothing. Rather, over the switching angle of 36° predetermined by the decimal advancing, a greater number of notches (not shown) can also be accommodated for the idle-stroke pawl 24, in order to effect an even greater stepping-down of the counting mechanism 1, in conjunction with a suitably adapted slotted link.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Theoretical Computer Science (AREA)
  • Transmission Devices (AREA)
  • Vehicle Body Suspensions (AREA)
  • Supplying Of Containers To The Packaging Station (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Labeling Devices (AREA)
US06/368,206 1981-04-27 1982-04-14 Stepped-down mechanical counting mechanism Expired - Fee Related US4419571A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3116629 1981-04-27
DE3116629A DE3116629C1 (de) 1981-04-27 1981-04-27 Antrieb des Einerrads eines untersetzten mechanischen Zaehlwerks

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US4419571A true US4419571A (en) 1983-12-06

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US (1) US4419571A (de)
EP (1) EP0064157B1 (de)
JP (1) JPS57187786A (de)
AT (1) ATE9743T1 (de)
DE (1) DE3116629C1 (de)

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1695964A (en) * 1925-11-07 1928-12-18 George H Lang Printing machine
US2966843A (en) * 1960-02-16 1961-01-03 Ncr Co Multiple rotatably settable member setting means
US3620447A (en) * 1970-09-08 1971-11-16 Veeder Industries Inc Counter
US3738264A (en) * 1969-06-13 1973-06-12 Olympia Werke Ag Type carrier setting device
US3927613A (en) * 1974-02-04 1975-12-23 Addressograph Multigraph Imprint wheel assembly
US4055116A (en) * 1976-02-17 1977-10-25 Emerson Electric Co. Counting and printing mechanism with interchangeable unit printer wheel
US4149460A (en) * 1976-04-10 1979-04-17 Kabushiki Kaisha Sato Kenkyusho Printing device for hand labeler
US4185188A (en) * 1978-09-28 1980-01-22 Bowmar Instrument Corporation Internal pinion revolution counter and method of assembling the same
US4343238A (en) * 1980-01-16 1982-08-10 Esselte Pendaflex Corporation Counting or printing mechanism for consecutive counting numbering

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1474715A (en) * 1921-11-26 1923-11-20 Bates Mfg Co Numbering machine

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1695964A (en) * 1925-11-07 1928-12-18 George H Lang Printing machine
US2966843A (en) * 1960-02-16 1961-01-03 Ncr Co Multiple rotatably settable member setting means
US3738264A (en) * 1969-06-13 1973-06-12 Olympia Werke Ag Type carrier setting device
US3620447A (en) * 1970-09-08 1971-11-16 Veeder Industries Inc Counter
US3927613A (en) * 1974-02-04 1975-12-23 Addressograph Multigraph Imprint wheel assembly
US4055116A (en) * 1976-02-17 1977-10-25 Emerson Electric Co. Counting and printing mechanism with interchangeable unit printer wheel
US4149460A (en) * 1976-04-10 1979-04-17 Kabushiki Kaisha Sato Kenkyusho Printing device for hand labeler
US4185188A (en) * 1978-09-28 1980-01-22 Bowmar Instrument Corporation Internal pinion revolution counter and method of assembling the same
US4343238A (en) * 1980-01-16 1982-08-10 Esselte Pendaflex Corporation Counting or printing mechanism for consecutive counting numbering

Also Published As

Publication number Publication date
EP0064157A1 (de) 1982-11-10
DE3116629C1 (de) 1982-11-11
EP0064157B1 (de) 1984-10-03
JPS57187786A (en) 1982-11-18
ATE9743T1 (de) 1984-10-15

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